FR2774441A1 - Friction clutch for motor vehicle - Google Patents

Abstract

The vehicle friction clutch play compensator has a cassette (10) carried by a cover (52) and ramps (54) placed between the contacts (14) for the clutch components and a pressure plate (51). The cassette has two side wings (65,66) each with a hole (61). The holes are offset axially to receive an endless screw (62) to actuate the ramps.

Description

 The present invention relates to a friction clutch, in particular for a motor vehicle, and relates more particularly to a clutch equipped with a device for compensating for wear due in particular to the wear of the friction linings, said device, known as after wear take-up device, operating progressively with the wear of said linings.

 It relates to the friction clutch mechanisms that such a clutch comprises.

 A conventional friction clutch generally comprises a reaction plate, possibly in two parts to form a damping flywheel or a flexible flywheel, fixed in rotation on a first shaft, usually a driving shaft such as the crankshaft of the combustion engine. internal, and supporting by its external periphery a cover to which is attached, with axial mobility, at least one pressure plate.

 The pressure plate is integral in rotation with the cover and the reaction plate while being able to move axially under the stress of axially acting engagement means controlled by declutching means. The declutching means may consist of helical springs, or two Belleville washers mounted in series, subjected to the action of declutching levers forming the declutching means.

 Generally, the engagement and disengagement means belong to the same part, for example a metal diaphragm bearing on the cover; the diaphragm can be mounted in series or in parallel with a Belleville washer to provide assistance with the clutch release force.

 A friction disc, carrying friction linings at its outer periphery, integral in rotation with a shaft, usually a driven shaft such as the input shaft of the gearbox, is interposed between the pressure plate and the reaction plate so as to be clamped together when the clutch is in the engagement position to transmit the torque from the drive shaft to the driven shaft.

 Conventionally, the friction linings are mounted on an axially elastic support rigidly or resiliently coupled to a hub wedged in rotation on the driven shaft. Thanks to this arrangement, the friction disc assists the diaphragm during the clutch release operation.

 Conventionally, the engagement means, the cover and the pressure plate belong to a unitary assembly known as a friction clutch mechanism.

 The clutch means control the axial movement of the pressure plate when they are actuated by a declutching stop by means of the declutching means.

 The clutch release bearing can be controlled mechanically, hydraulically or electrically. The control can be of the manual, automatic or semi-automatic type.

 During the lifetime of such a clutch, the friction linings as well as the counter-materials, pressure and reaction plates wear, which causes a variation in the position of the pressure plate and that of the means axially acting clutches and the clutch release bearing, which results in a variation in the clamping force between the friction disc, on the one hand, and the pressure and reaction plates, on the other hand, due to changes in the working conditions of the clutch means, and the force required to disengage is affected. By providing such a clutch with a wear take-up device, these drawbacks are avoided, the clutch means, as well as the clutch release bearing, usually in constant support on the clutch means, occupying the same position when the clutch is in engagement position.

 In document FR 96 11297 filed on September 17, 1996, the wear take-up device comprises, in FIGS. 21 to 26, a cassette unitarily comprising a U-shaped support with a core and two lateral wings each provided with a hole for supporting at least one axis carrying a worm, a ratchet wheel and a helical spring. The support further carries an elastic member provided, on the one hand, with a control tab and, on the other hand, with a non-return pawl.

 The control tongue is adapted to be maneuvered by an actuator belonging to the clutch engagement means of the clutch and cooperates, like the pawl, with the teeth of the ratchet wheel.

 The worm cooperates with the teeth of a toothing belonging to ramp means placed between the support means of the engagement means and the pressure plate. The worm cooperates with the teeth and with rotational drive means, comprising the helical spring, which are made operational by the wear of the friction linings when the clutch is engaged. The worm is mounted tangentially relative to its associated toothing.

 It is desirable to improve the cooperation of the screw with the teeth.

 The object of the present invention is to respond to this wish in a simple and economical manner.

 According to the invention a clutch mechanism of the above-mentioned type is characterized in that the holes of the wings are offset axially with respect to each other.

 So we can tilt the axis and therefore the worm.

 Preferably the axis is inclined at an angle equal to that of the thread of the worm. The inclination depends on the angle of the worm.

 More precisely, the profile of the screw, in particular the thread thereof, moves overall to the sides of the teeth of the teeth. The face of the thread is therefore generally parallel to the flank facing the tooth.

 Thanks to the invention, the risks of jamming between the screw and the toothing of the ramp means are eliminated.

 In addition, a good contact area between the screw and the teeth is obtained, the teeth of which are thus straight.

 The performance of the wear take-up device is high.

 Admittedly, the cassette could have been tilted directly, but this would have increased the size of the latter and therefore increased the size of the housing produced in the cover for mounting the cassette.

 Thanks to the invention, the overall dimensions of the cassette remain generally the same. In addition, the support is not deeply modified.

 The solution is therefore simple and economical.

 In a first embodiment, the wings are twisted to present inclined zones perpendicular to one axis.

 Twisting is simple and economical. In addition, the number of pieces is not increased.

 In another embodiment, the wings are not twisted so that the support is not modified.

 The inclination is carried out using bearings whose central hole is inclined. The bearings are mounted in the wing holes.

 The holes are advantageously blind at the start and then partially closed by crimping tabs in contact with the bearings for automatic mounting and / or formation of a single part, axis - screw - ratchet wheel.

 Depending on the desired inclination of the worm, the teeth of the ratchet wheel are also inclined cooperating with one end of the control tongue and a non-return pawl which the elastic member comprises.

 Thanks to this arrangement, the free end of the control tongue extends parallel to the teeth of the ratchet wheel and the non-return pawl is twisted, due to its offset with respect to the control tongue, so that its end free is parallel to the teeth.

 Thus, despite the inclination of the axis, there is a good transmission of forces between the engaging means and the ratchet wheel, and the non-return pawl has a large contact area with the teeth of the ratchet wheel.

 Thanks to the invention, despite the inclination of the axis, we work with parallel faces, the thread of the screw being generally parallel to the flanks of the teeth of the teeth, while the free ends of the pawl and of the control tongue are parallel to the teeth of the ratchet wheel.

 The wing holes are not necessarily the same size.

 For example, the axis may have a portion of reduced diameter passing through a hole of reduced size made in one of the wings and immobilized axially using an elastic washer.

 A cylindrical extension of the worm then passes through the other larger hole of the other wing.

 The elastic member has a return carrying the control tab centrally.

 According to one characteristic, the return presents on either side of the tongue a first and a second section of different height.

 This return has a non-symmetrical shape, the first section being opposite the screw and has a height less than that of the second section located opposite the helical spring.

 The return is thus mechanically resistant.

 This resistance is increased by the fact that the control tab is provided with an oblong-shaped reinforcement stamp. The stamp is also in the force transmission line between the engaging means and the ratchet wheel, which is favorable for driving the rock wheel t.

 This wheel has teeth inclined according to the thread of the worm.

 The operating tab and the non-return pawl, whose free ends are inclined, work in very good conditions.

 Thus in the event of wear on the linings, the helical spring can be armed under good conditions and then, subsequently, this spring, during the declutching operation, can cause the ramp means under very good conditions.

 Thanks to all these provisions, the wear take-up device has a high efficiency and a long service life.

To better understand the object of the invention, there will now be described, by way of purely illustrative and nonlimiting example, an embodiment shown in the accompanying drawings in which
- Figure 1 is a front view of a clutch equipped with a wear take-up device according to the invention, with local cut-outs to show the toothing of the ramp means and the tangential tongues
- Figure 2 is a sectional view along line A-Ade Figure 1
- Figure 3 is a sectional view along line BB of Figure 1
- Figures 4,5,6 are views on a larger scale respectively along the arrows C, D, E of Figure 1
- Figure 7 is an enlarged view of the insert T of Figure 2
- Figure 8 is a perspective view of the wear take-up cassette
- Figure 9 is a perspective view along arrow 9 of Figure S
- Figure 10 is a view along arrow 10 of Figure 8
- Figure 11 is a sectional view along line 1111 of Figure 10
- Figure 12 is a sectional view along line 1212 of Figure 11;
- Figure 13 is a view of the cassette support according to arrow 10 in Figure S
- Figure 14 is a view of the ratchet wheel endless screw assembly;
- Figure 15 is a perspective view of the elastic member carried by the support
- Figure 16 is a view along arrow 16 of Figure 15
- Figure 17 is a perspective view of the ramp means of the wear take-up device
- Figures 18 and 19 are views similar to Figures 10 and 12 for a second embodiment of the tilted axis cassette
- Figures 20 and 21 are views similar to Figures 10 and 12 for a third embodiment of the tilted axis cassette
- Figure 22 is a partial view showing, in the context of the third embodiment, the hole of a wing of the support of the cassette receiving its bearing before the fixing thereof
- Figure 23 is a view similar to Figure 2 for a fourth embodiment
- Figure 24 is a view similar to Figure 13 for this fourth embodiment
- Figure 25 is a sectional view along line 2525 of Figure 24
- Figure 26 is a view of the support according to arrow 26 of Figure 23
- Figure 27 is a partial view with local cutaway according to arrow 26 in Figure 23
- Figures 28 to 30 are views similar to Figures 9,10 and 7 respectively for a fifth embodiment
- Figure 31 is a view along arrow 31 of Figure 28
- Figures 32 and 33 are views similar to Figures 6 and 9 for a sixth embodiment, part of the ramp means being shown in Figure 32.

 In the figures, the common elements will be assigned the same reference signs.

 The figures represent a clutch fitted with a wear take-up device, of the type described in the French patent application filed on September 17, 1996 under the number 96 11297 to which reference should be made for more details.

 Referring to the figures, there is seen a friction clutch mechanism, in particular for a motor vehicle, of axis of axial symmetry XX, which forms a unitary assembly and which comprises a pressure plate 51 intended to cooperate with a friction disc. (shown schematically in Figure 7 in 100), carrying at its outer periphery friction linings, which itself cooperates with a reaction plate. The reaction plate, shown diagrammatically at 101 in FIG. 1, is intended to be locked in rotation on a driving shaft, such as the crankshaft of the internal combustion engine.

The friction disc is integral in rotation with a driven shaft such as the input shaft of the gearbox.

 The pressure plate 51 is integral in rotation with the cover 52 by means of tangential tongues 9, one of which is visible in FIG. 4 and which, axially elastic, at the same time constitute means for returning the pressure plate 51 to the cover 52.

 The tongues 9 are fixed by riveting at one of their ends to the cover and at their other ends to a tab 251 of the pressure plate (FIG. 4).

 The tongues 9 allow an axial movement of the pressure plate 51 relative to the cover 52. The cover is metallic by being in pressed sheet metal. This cover 52 has a bottom, of transverse orientation, drilled centrally and means 152 for fixing it to a reaction plate, possibly divided to form a damping flywheel.

 Here the cover 52 is generally in the form of a hollow plate and has at its external periphery a radial flange 152 forming the means for fixing the cover to the reaction plate, said flange being provided with holes for passage of fixing members, such as screws, from cover to reaction plate.

 An annular skirt of axial orientation connects the bottom to the rim and is open at the level of the tongues 9 (FIG. 4).

 Here the reaction plate 101 is flat. As a variant, this plate has a skirt on which the flange 152 is fixed so that the cover 52 can be shallower.

 The pressure plate 51, while being integral in rotation with the cover 52, is therefore axially displaceable relative to the cover 52 under the stress of axially acting engagement means controlled by declutching means, here a diaphragm 53 mounted articulated on the cover 52 thanks to small columns 58 carried by the bottom of the cover 52 with a hole in the center.

 The diaphragm 53, forming elastic means with axial action, has a frustoconical shape in the free state and has a peripheral part in the shape of a Belleville washer extended towards the center by a central part fragmented in radial fingers by slots as visible in the figure. 1.

 The diaphragm 53 is supported, by means of its Belleville washer, on the bottom of the cover for action on the pressure plate 51 and clamping of the friction linings, which the friction disc has, between the pressure and reaction plates .

Here the clutch is of the pushed type, that is to say, using a clutch release bearing, controlled manually or semi-automatically or automatically and not shown, act by pushing on the internal end of the fingers of the diaphragm 53 to disengage (disengage) the clutch. To do this (Figure 2), the bottom of the cover 52 carries, on the one hand, a primary support consisting for example of a rod, or here in a stamped formed in the bottom of the cover at the inner periphery thereof and , on the other hand, opposite the primary support, a secondary support in the form of a rolled crown carried by the balusters 58, or any other means. The diaphragm 53, by the internal periphery of its washer
Belleville, is pivotally or pivotally mounted between said primary and secondary supports. By the outer periphery of its Belleville washer, it is in contact with support zones 14, described below. These zones 14, forming support means, are carried by the pressure plate 51.

 To maintain, when the clutch is engaged, the axially acting clutch means 53 in a position independent of the wear of the linings of the friction disc, and to a lesser extent the wear of the pressure and reaction plates 51 whose so-called friction surfaces wear out in contact with the disc linings, a wear take-up device 10 is provided.

 The wear take-up device comprises a cassette 10 and ramp means 54 arranged circumferentially; more specifically, these ramp means 54 consist of a sheet metal ring cut and stamped so as to have ramps 56 arranged circumferentially; said ring also has bearing zones 14 constituted by the rounded upper edge of stamped arcs of a circle centered on the axis of the clutch and placed radially outside with respect to the ramps 56 (FIGS. 2 and 17 ).

 The pressure plate 51 has here, coming from molding, on its face turned towards the bottom of the cover 52, radially beyond the balusters 58, studs 57 distributed circumferentially at a distance from one another which corresponds to that which circumferentially separates two successive ramps 56, the studs 57 being intended to cooperate each with a ramp 56.

 The rim 152 has areas offset axially in the direction of the bottom of the cover for carrying balancing rivets 1 (FIG. 5) for balancing the clutch mechanism comprising unitarily the cover 52, the pressure plate 51, the diaphragm 53 and the wear take-up device.

 The ramp means 54 are placed axially between the diaphragm 53 and the pressure plate 51 so that the studs 57 receive the ramps 56 and that the diaphragm 53 cooperates with the support zones 14 which thus constitute the support means, here fractionated in a continuous variant, via which the diaphragm 53 acts on the pressure plate 51. This arrangement is economical and simple, the ramp means 54 being metallic and obtained by stamping. As a variant, the studs 57 are replaced by counter-ramps of the same shape as the ramps 54.

 At least one of the bearing zones 14 of the ramp means 54 is extended at its external periphery by a flange parallel to the axis of the clutch ending in a transverse return, that is to say s' extending in a plane perpendicular to the axis XX of the clutch, provided at its external periphery with a toothing 59, so that the bearing zones 14 can be continuous and that the flange is centered by an extra thickness 157 of the plate pressure 51.

 It is in each additional thickness 157 that the studs 57 are formed. All the additional thicknesses 157 can participate in the centering of the ring 54 having a continuous rim. As a variant, all the extra thicknesses 157 do not participate in centering. Likewise, the edge of the ring 54 may not be continuous. This ring 54 therefore comprises a smaller number of centering zones than there are pads 57, knowing that each centering zone is associated with a ramp 56.

 Advantageously, the studs 57 and therefore the extra thicknesses 157 are chamfered to cooperate in a complementary manner with the ramps 56. In all cases the studs 57 form counter-ramps.

 The number of pads 57 and ramps 56 depends on the applications, the same is true of the complementary centering zones formed respectively at the outer periphery of the pads 57 and at the inner periphery of the axial rim (s) of the ring 54.

 Thus twelve ramps 56 and pads 57 can be provided.

Twelve extra thicknesses 157 can form a centering zone in association with twelve centering zones belonging to the ring.

 As a variant, six extra thicknesses 157 can form a centering zone, the ring 54 having six centering zones and vice versa. The pressure plate 51 therefore carries the bearing zones 14 and the means with ramps 54 movable in rotation, while the pressure plate is fixed in rotation. This plate 51 thus has a variable thickness. More precisely, the distance between its front face, serving as a friction face for the friction disc 100, and the bearing zones 14 vary according to the aforementioned wear.

 Of course, the ramps and counter-ramps can be produced using the screw-nut system. For example, a ring carrying the support zones 14 has an internal thread for screwing onto an external thread of the pressure plate.

 The wear take-up device also comprises a ratchet wheel 60 with inclined teeth secured to an axle 67 which also carries an endless screw 63; the thread and the pitch of the worm 63 are adapted to the toothing 59; the worm 63 is brought to cooperate with the teeth 59 under the conditions which will be described below. The screw 63 extends tangentially with respect to the teeth.

 The axis 67 of the ratchet wheel 60 is rotated by a support 62, better visible in Figures 8 and 13, in cut and folded sheet metal, U-shaped having a core 64 and two wings 65,66 intended for support the axis 67. For this purpose, each of the wings carries a circular hole 61 (FIG. 12) adapted to receive it; the core 64 carries laterally a tab 68 at the square directed radially outwards and intended to be fixed on a range 154 of the outer rim 152 of the cover 52 by two rivets 155, said range being offset axially towards the bottom of the cover 52. The cover 52 has an opening 156 (FIG. 7) for passage of the core and is simplified.

 According to one characteristic, the core 64, of axial orientation, rests on the edge 158 of the opening 156 affecting the bottom of the cover 52. The core 64 can be fixed on the edge 158 belonging to the bottom of the cover 52, for example by bonding, welding or crimping.

 In the case of fixing by crimping, the core 64 is supported and passes through a notch made in the flange 158.

After crossing the rim, the lateral ends of the core are hot-pressed to carry out the crimping.

 More precisely, the core 64 of the support 62 has, on the side opposite that on which the tab 68 is located, an axial extension 170 intended to be fixed to the bottom of the cover 52. This extension is provided with returns 71 extending generally perpendicular to the core 64 and intended to constitute control stops whose role will appear below; the ends of said returns 71 are at a sufficient distance from each other to allow, without interfering, the movement of the actuator 55 during clutch and declutching operations.

 The actuator 55 is constituted by a protuberance (or appendage) which comprises the diaphragm 53 radially projecting at its external periphery.

 In practice the returns 71 extend radially above the actuator 55 and are inclined (Figures 7,8,9 and 13). These returns 71 are produced by cutting and folding the axial extension 170 of the core 64, which has been hatched in Figure 13 its flat area. The returns 71 are thus arranged on either side of an axial tab 171 and are separated from the latter by notches with a semi-circular bottom 172.

 This tab 171 extends in axial projection with respect to the returns and is in abutment at its free end against the edge 158. This tab 171 is fixed at its free end to the edge 158 in the aforementioned manner for example by welding, as visible on the Figure 7. The edge 158 forms a bearing surface for the tab 171.

 The support 62 is thus simple in shape and is stable.

 It is much simpler than that described in the aforementioned document FR 96 11297 because the returns 71 do not come from the wings of the support. In addition, the tab 171 makes it possible to reduce the number of fixing rivets and is a fixing and stabilization tab.

 Thanks to the invention, the number of fixing lugs on the cover is reduced.

 Given the opening 156 affecting the cover 52 at the connection zone of the skirt of the cover to the bottom of the cover, welding, bonding or crimping the tab 171 at the edge 158 of the opening is easy.

 The support 62 is adapted to receive an elastic member 72.

 Here, the elastic member 72, better visible in FIG. 15, is in the form of a jumper and comprises an elongated plane body 73 carrying at each of its ends an arm 74 provided with a hole 75 adapted to receive the axis 67; the two arms 74 are parallel, as described below, and extend on the same side and generally perpendicular to the body 73.

 On one of its longitudinal edges, the body 73 extends in an oblique extension 84 on the same side as that where the arms 74 are placed; notches 82 and 83 formed in the body 73 limit the extension 84 relative to the ends of the body 73 carrying the arms 74; moreover, these notches 82 and 83 give the extension 84 a certain elasticity.

 The free end of the extension 84 is provided with a return 85 which extends along a control tab 76 extending in the direction of the body 73 while being generally parallel to the latter.

 A cutout 77 is provided in the extension 84; by means of this cutout 77 and notches 79 and 80 in the body 73, a non-return pawl 78 in the form of a blade is produced. The free end of the pawl 78 extends generally perpendicular to the body 73.

 Here, as best seen in FIG. 11, the control tongue 76 and the pawl 78 are slightly inclined respectively with respect to the plane of the body 73 and to the plane perpendicular to the plane of the body 73.

 The pawl 78 is offset from the tongue 76, the free ends of the pawl 78 and the tongue 76 being circumferentially offset.

 A helical compression spring 86 is placed between the ratchet wheel 60 and the free end of the arm 74, being wound around the axis 67; the worm 63 and the ratchet wheel 60 are cut in one piece.

 The ratchet wheel 60 is located between the screw 63 and the spring 86.

 The helical spring 86 constitutes the elastic take-up means; the ratchet wheel 60 is in line with the non-return pawl 78 which, by cooperation with the inclined teeth of the ratchet wheel 60, prevents the ratchet wheel 60, as well as the worm 63, from turning in the opposite direction to that of clockwise, with respect to FIG. 1.

 The support 62, carrying the ratchet wheel 60, the worm 63 and the helical spring 86, being integral with the cover 52, the diaphragm 53 moves relative to it during the declutching and re-clutch operations; the diaphragm 53 carries at its periphery a radial appendage (or radial protuberance), called actuator 55, extending radially outside the Belleville washer part of the diaphragm 53 to cooperate with the extension 84 of the elastic member 72, more precisely with a rounded zone 184 connecting the main part of the extension to the return 85 (FIG. 7); it will be understood that, thanks to this arrangement, during the tilting of the diaphragm 53 during declutching and re-clutching operations, the actuator 55 moves the extension 84 from right to left, relative to FIG. 1, and the tongue control 76, by cooperation with the teeth of the ratchet wheel 60, is caused to rotate the ratchet wheel 60 clockwise and therefore to rotate the screw 63 by compressing the spring 86; when the actuator 55, on the return, is moved from left to right, the elasticity of the extension 84 of the elastic member 72 and the inclination of the teeth cause the tongue 76 to move to the right while rising on the teeth which are kept fixed in rotation by the non-return pawl 78.

 The operation of the play take-up device which has just been described is known and will not be detailed; if necessary, reference may be made to the French patent application 96 11 297 already cited, the part of the corresponding description of which must be considered to be part of the present application, knowing that during the declutching operation the return stroke or for arming the control tab 76 is limited by abutment of the extension 84, more precisely of the rounded zone 184, against the returns 71 of the support 62 which is thicker than the member 72.

 The returns 71 (271 in the other figures) have the role of providing the elastic member 72.

 Here, the worm 63 and the ratchet wheel 60 are in one piece and are forced to be pushed onto the axle 67 carried by the support 62. The axle 67 is grooved for its press fit into the piece 60 , 63 and passes through the holes 61 of the wings 65 and 66 of the support 62. A crew is thus formed - axle 67, wheel 60, screw 63, spring 86 - carried by the wings 66,65. Here the axis 67 is therefore integral with the one-piece worm 63 - ratchet wheel 60 assembly, which is axially immobilized by the two arms 74 and the two wings 65, 66 respectively of the elastic member 72 and of the support 62 To do this, the arms 74 have a free end in the shape of a washer 174 (FIG. 15) perforated at 75.

 One of the washers 174 is interposed axially between the internal face of the wing 65 and the free end of the worm 63, here extending over less than two turns, here 1/25 of turns, while the other washer 174 is interposed between the internal face of the wing 66 and the free end of the helical spring 86.

 I1 is thus formed in a unitary manner a cassette 10 which can be handled and transported comprising parts, all of which are metallic here, namely the support 62, the elastic member 72, the helical spring 86, the ratchet wheel 60, the worm 63 and the axis 67, knowing that the elastic member 72 (FIGS. 8 and 11) has at its end opposite the extension 83 a lug 168 of radial orientation attached to the lug 68 of the support 62. The body 73 is attached to the core 64. The tab 168 has, like the tab 68, two holes for the passage of fixing rivets 155.

 Note that the outer periphery of the pressure plate 51 is locally notched for housing the cassette 10 (Figure 7) and reduction of the axial size.

 Of course, a housing 110 is formed in excess thickness, here by press deformation, at the level of the region 154 of the rim 152 of the cover 52 for mounting the cassette 10 (FIGS. 1 and 7).

 The housing 110 is delimited by the area 154 secured to a central orientation core (not referenced), the end opposite to the area 154 is provided with the opening 156.

 Here three housings 110 are provided, as visible in FIG. 1. A single housing is used for mounting the cassette 10.

 Two inclined lateral portions 111 connect the core to perforated areas of the rim 152 for the passage of the fixing members of the cover to the reaction plate.

 The housing 110 protects the cassette 10 and is open at the level of the track 154.

 Cutouts (not referenced) are made in the portions 111 extending on either side of the central core of the housing 110. The ends of the axis 67 protrude from the wings 65,66. The axis 67 has a slot 167 at its protruding end of the wing 65. There is thus created means for resetting the wear take-up device to zero.

 For this reset, a tool is not visible.

 This tool may be in the form of a screwdriver, the blade of which penetrates into the slot 167. As a variant, the tool consists of a rod, one end of which carries an operating button, for example knurled, and the other end of which is flat for enter the slot 167.

 The cuts made in the portions 111 of the cover 52 make it possible to define a passage in alignment with the axis 67 for the passage of the tool.

 The operation of resetting the wear take-up device to zero easily follows from the above description.

For more details, see the document
FR 97 06655 of May 30, 1997 showing a form of tool.

 When the tool is in place, the rotation setting of the worm screw 63 relative to the tool allows, by turning the tool, to rotate the worm screw 63 relative to the cover 52, therefore the toothing 59 relative to the pressure plate 51, and the ramps 56 relative to the studs 57.

 The circumferential length of the toothing 59 corresponds to the amount of wear that it has been decided to take up, obviously taking into account the few teeth with which the worm 63 meshes in the initial state.

 When the amount of wear chosen corresponding to the circumferential length of the toothing 59 has been taken up, the worm 63 no longer cooperates with the toothing 59.

 When changing the friction disc, to reset the wear take-up device, it suffices with any tool to rotate the ramp means 54 around their axis so that the ramps 56 mount on the pads 57 up to that the first tooth of the toothing 59 meets the first thread of the worm 63; by rotation of the worm 63 by means of the zeroing tool, we then engage a few first teeth of the toothing 59 with the threads of the worm 63.

 The angle by which the ramp means 54 must be rotated in the first phase of zeroing depends on the number of wear take-up devices; usually there is only one wear take-up device so that the angle is large.

To minimize this angle regardless of the number of devices, it is possible to provide a toothing 59 composed of several toothing elements such as the elements 59A, 59B, 59C shown in FIG. 17: advantageously as mentioned above, there are as many toothing elements as ramps 56, each element corresponding to the chosen wear of a friction disc; the ramps 56 are opposite the teeth elements 59A, 59B, 59C.

 Of course the elastic member 72, here metallic, is of thickness less than that of the support 62 in order to make flexible the pawl 78 and the control tongue 76 which has a boss 176 centrally, here of oblong shape. Thanks to this boss 176 all the mechanical stresses are brought back towards the center of the tongue 76 so that the tongue 76 is less fragile. This arrangement increases the life of the tongue 76, the boss 76 being a stamped.

 As better visible in FIG. 14, the teeth of the ratchet wheel 60 are inclined relative to the axis ZZ of axial symmetry of the ratchet wheel 60 - worm 63 assembly. The teeth of the wheel 60 are at right of the pawl 78, forming a non-return pawl, and of the control tab 76.

 According to a characteristic of the invention the axis 67 and therefore the monobloc assembly 63 - wheel 60 is inclined.

 In all the figures, this inclination is achieved by an axial offset from the centers of the holes 61 of the wings 66, 65 perpendicular to the core 64.

 More specifically (Figures 1 to 17) the center of the hole 61 of the wing 65 adjacent to the screw 63 is closer axially to the bottom of the cover 52 than is the center of the hole 61 of the wing 66 adjacent to the spring 86. The inclination of the axis 67 and therefore of the screw 63 is a function of the inclination of the thread and of the pitch of the screw 63.

 Here the screw 63 - toothing 59 system is irreversible, the screw 63 can cause the toothing 59 but not the reverse.

 Here the angle of inclination of the axis 67 is generally an angle equal to that of the thread of the worm.

 Thanks to this arrangement, the teeth of the toothing 59 are straight which facilitates the entrainment drive and avoids any jamming, the contact surface between the thread of the screw 63 and the teeth of the toothing being maximum. The axis 67 is therefore inclined relative to a plane perpendicular to the axis of axial symmetry X-X of the clutch and of the clutch mechanism, knowing that the screw 63 extends tangentially with respect to the teeth 59.

 Thanks to these arrangements, the toothing 59 - worm 63 system is of good performance, the thread of the screw extending generally parallel to the flanks of the teeth of the toothing.

 The teeth of the ratchet wheel 60 are inclined as a function of the inclination of the axis 67 corresponding to the angle formed between them by the lines V-V and Y-Y in FIG. 13.

 More precisely, a straight (parallel) contact is sought between, on the one hand, the teeth of the ratchet wheel 60 and, on the other hand, the non-return pawl 78 and the control tongue 76. This results, according to a feature of the invention, that the free end of the pawl 78 is inclined at an angle as a function of the inclination of the axis 67, itself dependent on the thread of the worm 63. This inclination is visible for example in Figures 8,15,16.

 This inclination depends on the circumferential offset between the free ends of the pawl 78 and the tongue 76 (Figures 7 and 11).

 The contact zones between the teeth of the wheel 60 and the free ends of the pawl 78 and of the tongue are maximum and linear.

 The pawl 78 and the tongue 76 bear over the entire surface of the tooth concerned of the ratchet wheel.

 More precisely thanks to the inclination of the teeth of the ratchet wheel, the free end of the control tongue 76 is parallel to the tooth opposite the ratchet wheel 60, therefore to the teeth of said wheel.

 By cons, due to the offset of the pawl 78 relative to the tongue 76, the free end of the pawl 78 is then not parallel to the tooth opposite the wheel 60 if care is not taken.

 Thus, as best seen in Figures 15 and 16, the pawl is twisted to account for this offset. This twist leads to tilt the free end of the pawl 78 relative to the right free end of the control tab 76.

 The pawl 78 is therefore twisted to cooperate in a straight manner, that is to say in parallel with the teeth of the ratchet wheel 60.

 Thanks to these provisions, the contact area between the actuator 55 and the elastic member 72 is maximum, knowing that in the engaged clutch position the diaphragm is generally in a plane perpendicular to the axis XX of the clutch mechanism and of the 'clutch.

 The elastic member 72 is in linear contact through its rounded zone 184 with the entire surface of the actuator 55 of the diaphragm and this in all the positions of the diaphragm.

 When the clutch is re-engaged, good force transmission is obtained, thanks in particular to the stamped 176 forming a boss, with maximum contacts between, on the one hand, the actuator 55 and the elastic member 72 and, d on the other hand, between the teeth of the wheel 60 and the control tongue 76. The wear take-up device therefore has a further improved efficiency with risks of jamming further minimized.

 According to one characteristic, the return 85 of the elastic member 72 has a non-symmetrical shape which takes account of the inclination of the axis 67 of the parts 63, 60, 86 located between the two wings 66, 65.

 The return 85 carries centrally projecting the tongue 76 and has two sections on either side of the tongue.

 The first section located opposite the screw 63 is lower than the second section located opposite the take-up spring 86.

 Thus the return 85 has a maximum mechanical resistance in connection with the stamped 176 allowing good transmission of the forces since it is perpendicular to the rounded zone 184.

Of course, the free end of the tongue 76 and of the pawl 78 is narrower than the teeth of the screw 60.

 Here the wings 65 and 66 are twisted, as well as the arms 74, to tilt the axis 67 as a function of the thread of the tangential screw 63.

 More precisely, the free ends of the wings 65 and 66 and of the arms are inclined by being perpendicular to the axis 67 of line of symmetry YY inclined with respect to a line V situated in a plane perpendicular to the axis XX and to the core. 64 (Figure 13).

 Thus the wings 65, 66 have a main part perpendicular to the core 64 and at the level of the holes 61 of the inclined zones 165, 166 parallel to each other and perpendicular to the line YY and to the axis 67. The zones 165, 166 are inclined towards the inside the core 65 and have the holes 61.

 Thanks to this arrangement, the space requirement is not increased excessively.

 Likewise, the end washers 174 of the arms 74 of the member 72 are inclined and parallel to one another and to the zones 165, 166.

 Thus the cassette 10, in particular the support 62 thereof, has a smaller footprint than if the entire cassette had been tilted, while being simple in shape.

 Of course (Figures 18,19), the axis 67 may not be integral with the screw 63 - wheel 60 assembly.

 In this case, without modifying the wings 65, 66, it suffices to reduce the size of the holes presented by the inclined zones 165, 166 of the wings 65, 66.

 Thus the axis 67 has an end of reduced diameter 267 passing through the washer 174 and a hole 161 in the inclined area 166 of the wing 66. The axis enters the bore of the one-piece part 63.60.

 The screw 63 has a cylindrical extension 163, of diameter greater than that of the axis passing through the washer 174 and a hole 261 of the inclined zone 165 of the wing 65. The lathe 261 has a diameter greater than that of the hole 161 and the extension 163 has a slot 367 in order to be able to turn the screw 63 using a tool and carry out the reset as in FIGS. 1 to 17.

 The axis 67 is immobilized axially thanks to the shoulder formed by its change in diameter and in contact with the face of the washer 174 facing the spring 86 and to an elastic washer 2 having arms in contact with the end 267, said washer 2 being in contact with the external face of zone 166 of wing 66.

 The holes 161, 261 are offset axially with respect to each other. The part 60-63 turns on the axis immobilized also in rotation by the washer 2.

 In general, the equipment of the parts 63, 60, 86, 87 is carried by the holes 66, 65 holes and the axis 67 crosses at least the hole 61, 161 of one of the wings 66, 65.

 As a variant (FIGS. 20,21) the wings 65,66 are not twisted as are the arms 74. The holes 361 made in the wings 65,66 are axially offset and have the same size for mounting a shouldered bearing 3 with holes centrally.

 The bearing 3, advantageously of moldable material or of sintered material, with a low coefficient of friction such as plastic, has a change in diameter for the formation of a shoulder allowing the arm 74 concerned to be axially immobilized between said shoulder and the inner face of the wing 65,66 concerned.

 The central hole of the bearing 3 is inclined according to the applications. The axis crosses the bearings 3.

 Thus, thanks to the inclined central holes of the bearings 3, the axis 67 is inclined by the desired value for maximum contact between the tangential screw 63 and the teeth of the toothing 64. As in all the figures, the thread of the screw 63 has a trajectory (a displacement) parallel to that of the teeth of the toothing 59, the dorsal faces of the bearings are inclined so as to be parallel respectively to the end face of the screw 63 and to the end of the spring 86.

 The axis 67 has slots 167 for resetting, the axis 67 being press fitted as in Figures 1 to 17 in the part 60,63.

 Of course, the axis 67 can be in one piece with the wheel 60 and the screw 63. In this case (FIG. 22), the through holes made in the wings 65, 66 must be opened.

 Thus the hole 461 can initially be a blind hole (FIG. 22) with a semi-circular bottom. This hole 461 has a U shape and is delimited by two tabs 462 which are then folded down to trap the bearing 3.

 The bearing 3 is therefore fixed by crimping thanks to the tongues 462, on its associated wing. This type of embodiment also applies to the case where the axis is not inclined. This promotes automatic mounting of all of the parts 3,60,63,67,86 on the wings. This assembly is simple and quick.

 Of course, FIGS. 23 to 27, as a variant, the wings 66, 65 can carry the returns 71 and come into contact with the edge 158 of the opening 156 which is then radially higher, the diaphragm 53 being mounted with articulation on a stamped cover and on the heads of the balusters profiled accordingly. The returns 71 are directed towards each other and are inclined relative to the wings 66,65.

 The solution is compact.

 The wings can be welded to the edge 158 forming a bearing surface for the wings 66.65.

 In general, the number of fixing lugs on the cover is further reduced.

 Of course one can reverse the structures, the axis 67 or the screw 63 has projections to be driven by a tool having slots for receiving the projections.

 The fixing means 152 of the cover 52 on the reaction plate can be constituted by the skirt of the cover 52 fixed directly on the reaction plate, for example by crimping.

 Generally it is possible to form a module comprising the reaction plate, the friction disc, the friction linings of which are interposed axially between the reaction plate and the pressure plate of the friction clutch mechanism, the cover of which is then fixed by its fixing means 152 in a detachable or non-detachable manner on the reaction plate.

 It is for this reason that we see in Figure 1 holes in the fingers of the diaphragm. These holes allow the passage of at least one screwing tool to cooperate with the heads of the screws for fixing the reaction plate, possibly in two parts, to the crankshaft of the motor vehicle engine.

The reaction plate can then belong to a double damping flywheel comprising a first mass fixed on the crankshaft and carrying a bearing, such as a ball bearing, carrying the reaction plate with holes for passage of the screwing tool or tools as described in the document
FR-A-2 716 511 with radial springs coupling the first mass to the reaction plate.

Of course, the axially acting engagement means may have another shape and include two washers.
Belleville mounted in series with declutching means in the form of levers as described in document FR 96 11058 filed on September 5, 1997. The screw 63 and the wheel 60 may be in two parts integral in rotation with one another.

 The axis 67 is engaged inside a central hole of the screw 63 or integral with the screw 63. Generally the axis 67 extends the screw 63. The support zones 14 can be connected to each other.

 In all cases, support means 14 are provided which, as a variant, may be distinct from the ramps 56 by being connected to the latter as described in document FR-A-2 684 151.

 The presence of the arms 74 of the elastic member 72 is not essential, the elastic member being able to be fixed for example by welding points to the core 64.

 Thus in FIGS. 28 to 30, the elastic member 72 bears directly on the bearings 3 more precisely on the larger part 30 of the bearing 3, the dorsal face of which is inclined as can be seen in FIG. 29.

 The member 72 bears on the top of the parts 30 and this resiliently.

 The part 30 is therefore of variable width, as in FIGS. 20 and 21, in which the larger part is not referenced.

 The screw 63 - ratchet wheel 60 - axle 67 assembly is in one piece and is mounted with the spring 86 and the two bearings between the wings 65, 66 not twisted.

 The two parts 30 of the bearings are in contact with the internal faces respectively of the wings 66, 65.

 The reduced diameter portions 31 of the bearing 3, made of moldable plastic or sintered material, are threaded into the blind holes 461 of the type of those of FIG. 22, then the tabs 462 are folded down to lock the bearings 3 axially.

 It will be noted that the free end 471 of the fixing and stabilizing tab is offset radially towards the axis relative to the core 64.

 Thus, the opening 356 is higher than that of FIG. 7, which makes it possible to produce the latter easily with the press, the material of the opening being easily removed.

 The same is true in Figure 23.

 The axial end 471 therefore bears on the bearing edge 158 of the opening 356 and is fixed thereto.

 Of course, FIGS. 32 and 33, rear fixing lugs 371 can come from the wings 65,66 as in document FR 96 11297. The lugs 371 extend perpendicular to the wings 66,65 outside the support 62.

The front fixing tab 268 is narrower than the front fixing tab of the previous figures and has only one hole.

 The attachment to the cover 52 is carried out using three fixing lugs 271,268 and three rivets.

 The returns 271 are identical to those of FIGS. 23 to 27, these returns from folding the wings 66, 65 are inclined.

 The wings 66, 65 are twisted over a greater length, the wing 65 being twisted outwards.

 In all cases the returns 71, 271 are control stops which spare the elastic member 72.

 In all cases, the contact faces (the free ends) of the twisted pawl 78 and of the tongue 76 work in parallel with the teeth of the wheel 60.

 It is the same for the screw 63 and the toothing 59.

 The pressure plate also advantageously has a clearance on its dorsal side to avoid any interference with the cassette.

 Thanks to the invention in the event of wear, precise operation is obtained in at least three phases.

 In a first phase, when the clutch is re-clutched, the tongue turns the wheel 60 and the pawl jumps a tooth. During the declutching operation following this first phase, nothing happens. A second phase of re-engagement begins during which the tongue 76 rotates the wheel 60 which then moves axially because the teeth 59 cannot rotate because of the load exerted by the diaphragm.

 The spring 86 is compressed. During the following declutching operation, a third phase begins where the spring can relax and rotate the teeth if there is not too much friction to overcome. Otherwise you have to start the operation again.

Claims (19)

 1- Friction clutch mechanism, in particular for a motor vehicle, comprising a cover (52), a pressure plate (51) linked in rotation to the cover (52) while being able to move axially relative to the latter, support means (14) carried by the pressure plate (51), axially acting engagement means (53) acting between the cover (52) and the support means (14), a wear take-up device comprising, on the one hand, ramp means (54) carrying an external toothing (59) and placed between the pressure plate (51) and the support means (14) carrying the ramp means (54) and, on the other hand, a cassette (10) carried by the cover (52) and comprising an endless screw (63) cooperating with the toothing (59) of the ramp means (54), in which the cassette (10) comprises a support (62) generally U-shaped with a core (64) and two lateral wings (65,66) each provided with a hole (61,161,261,361,461) for mounting in rotation of a equipment comprising the endless screw (63) on which is mounted an axis (67) passing through at least one hole (61,161,261,361,461) of one of the lateral wings, characterized in that the holes (61,161,261,361,461) are axially offset one by relative to each other for inclination of the worm (63) and the axis (67).  2- Mechanism according to claim 1, characterized in that the axis (67) and the screw (63) are inclined at an angle equal to that of the thread of the worm (63).  3- Mechanism according to claim 1 or 2, characterized in that the wings (66,65) are twisted.  4- Mechanism according to claim 3, characterized in that the free ends of the wings (65 and 66) are inclined so that the wings have inclined zones (165,66) parallel to each other and perpendicular to the axis (67) , said inclined areas being provided with holes (61,161 ...).  5- Mechanism according to claim 4, characterized in that the axis (67) has an end of reduced diameter (267) passing through a hole (161) in the inclined area (166) of one of the wings (66) and in that the worm (63) has a cylindrical extension (163) passing through the hole (265) passing through the inclined zone (165) of the other wing (65).  6- Mechanism according to claim 1 or 2, characterized in that bearings (3) perforated centrally are mounted in the holes (361) of the wings (65,66) and in that the central holes of the bearings are inclined for tilting the worm (63) and the shaft (67).  7- Mechanism according to claim 6, characterized in that the bearings (3) are shouldered and have inclined back faces.  8- Mechanism according to any one of claims 3 to 7, characterized in that one of the axis elements (67) - worm (63) is shaped to be rotated by a reset tool.  9- Mechanism according to any one of claims 1 to 8, characterized in that the support (62) carries an elastic member (72) provided with a control tongue (76) carried by a return (85) that has said elastic member and a non-return pawl (78), in that the non-return pawl (78) and the control tongue (76) are suitable for cooperating with a ratchet wheel (60) integral with the screw without end (63) and in that the return (85) of the elastic member has two sections of different height arranged on either side of the control tongue (76).  10- Mechanism according to claim 9, characterized in that a first of the sections is arranged opposite the worm (63) and has a lower height than the second section arranged opposite a helical compression spring, the worm (63) and the helical spring being arranged on either side of the ratchet wheel (60) being interposed between the two wings (65,66).  11- Mechanism according to claim 9 or 10, characterized in that the teeth of the ratchet wheel (60) are inclined according to the worm (63) and in that the non-return pawl (78) is twisted to cooperate in a straight manner with the inclined teeth of the ratchet wheel (60).  12- Mechanism according to claim 10 or 11, characterized in that the return (85) of the elastic member is connected to a rounded area (184) in contact with an appendage (55) of the engagement means with axial action (51) of the clutch.  13- Mechanism according to any one of claims 1 to 12, characterized in that the control tongue (76) has a boss (176) centrally.  14- Mechanism according to any one of claims 1 to 13, characterized in that the core (64) of the support (62) is extended axially to present a tab (171) penetrating into an opening (158) of the cover (52 ).  15- Mechanism according to claim 14, characterized in that said tab (171) is fixed on one of the edges (158) of the opening (56), for example by welding, gluing or crimping.  16- Mechanism according to claim 14 or 15, characterized in that two returns (71) are arranged on either side of the tab (171) to limit the movement of an elastic member (72) carried by the support ( 62).  17- Mechanism according to any one of claims 1 to 12, characterized in that the side wings (65,66) are engaged in an opening (156) formed in the cover (52).  18- Mechanism according to claim 17, characterized in that the lateral wings (65,66) are fixed to one of the edges (158) of the opening (156).  19- Mechanism according to claim 6 or 7, characterized in that the bearings (3) are engaged in blind holes (461) made in the wings (66,65) and locked by crimping (462) in said holes.